Rotary hydraulic torque converter



May 4, 1948. J. JANDASEK ROTARY HYDRAULIC TORQUE CONVERTER Filed June 30, 1943 3 Sheets-Sheet 2 uvmmm [Z -7Zz/ra asei.

A, x I v 7256 E BY y 1948. J. JANDASEK 2,440,825

ROTARY HYDRAULIC TORQUE CONVERTER Filed June 30, 1943 3 Sheets-Sheet 3 INVENTOR. Jaw J, xv i Patented May-'4. 1948 ROTARY HYDRAULIC TORQUE CONVERTER Joseph Jandasek, Highland Park, Mich assignor to Bendix Avia tion Corporation, South Bend,

Ind., a corporation of Delaware Application June 30, 1943, Serial No. 492,809

4 Claims. 1

This invention relates to transmissions and more particularly to fluid transmissions having flexibly mounted vanes, contoured to increase the over-all efliciency of the transmission.

Heretofore in the fluid transmission art it has been customary to employ fixed vanes or vanes mounted on shafts in such a manner that a force could be exerted on the vanes to rotate them to vary the angle at which the vanes contact or are contacted by the power transmitting fluid in the circuit to vary the power transmitting characteristics of the transmission. v

An object of this invention is therefore to provide a fluid transmission having resiliently mounted fluid deflecting vanes capable of assuming varying angular relations in accordance with variations of fluid reaction exerted on the vanes.

Another object resides in the provision of a fluid transmission having fluid deflecting vanes provided with resilient mountings and having contoured portions effective to deflect the fluid as it circulates through the power transmitting fluid circuit to increase the over-all efliciency of the transmission.

A further object is to provide a fluid transmission having flexible vanes adapted to assume varying contours under the influence of fluid reaction and centrifugal force exerted thereon to circulate the fluid through the power transmitting fluid circuit in a more efficient manner.

Yet a further object resides in the provision of fluid deflecting vanes having spaced fluid energizing and equalizing portions whereby the overall efliciency of transmitting power in a fluid transmission may be increased.

Another object of the invention is to provide a semi-free vane having a resilient mounting whereby the vane may assume varying angular relations in accordance with variations-of fluid reaction exerted thereon.

Another object of the invention resides in the provision of a fluid foil supported on a resilient mounting.

A further object of the invention is to provide an improved self-aligning entrance blade for an impeller, a turbine or a guide wheel of a fluid transmission operative to minimize frictional losses and shock in the operation of the transmission.

Another object of the invention is to provide a fluid transmission having independently operable entrance and discharge impeller, turbine and guide wheel units. I

Yet a still further object is to provide a transmission wherein discharge impeller and turbine units are directly connected to driving and driven shafts, and entrance impeller and turbine units are operably connected to the driving and driven shafts respectively through one-way clutches which render the entrance units operable automatically dependent on variations of speed of the driving and driven shafts.

Another object isto provide a fluid transmission including impeller and turbine units, and a guide wheel having independently operable entrance and discharge portions, means providing for free rotation of both portions with the impeller and turbine units when the transmission is operating as a fluid coupling and means for holding at least, one of the portions stationary when the transmission is operating as a torque converter. v

A further object of the invention resides in the provision of improved vanes and blades for impeller, turbine and guide wheel units.

Other objects and advantages of this invention will be apparent from the following detailed description considered in connection with the accompanying drawings, submitted for purposes of illustration only, and not intended to define the scope of the invention, reference being had for that purpose to the subjoined claims.

In the drawings wherein similar reference characters refer to similar parts throughout the several views:

Fig. 1 isa longitudinal sectional view of a fluid transmission embodying the invention;

Fig. 2 is a sectional view taken substantially on the line 2.--7 of Fig. 1;

Fig. 3 is a part sectional view of an embodiment of the invention similar in many respects to the embodiment illustrated in Figs. 1 and 2;

Fig. 4 is a part sectional view illustrating a modified form of the invention;

Fig. 5 is a sectional view taken substantially in. the line 5-5 of Fig. 4;

Fig. 6 is a diagrammatic view illustrating improved impeller blades in two operative positions;

Figs. 7 and. 8 are end and side elevation views of vane flexing means disclosed in Fig. 6;

Fig. 9 is a part sectional view of a modified form of impeller blade;

Figs. 10 and 11 are views similar to Fig. 9 showing the blade in varying operative positions;

Figs. 12 and 13 are diagrammatic views showing still further modified forms of semi-free vanes;

Fig. 14 is a part sectional view showing main vanes in two operative positions;

Fig. 15 illustrates an improved impeller entrance blade in two operative positions;

Fig. 16 is a part sectional view of a turbine semi-free vane, and

Fig. 17 is a part sectional view of an improved impeller main vane;

Fig. 18 is a diagrammatic view showing a further modified form of vane.

Before explaining in detail the present invention it is to be understood that the invention is not limited in its application to the details of construction and arrangement of parts illustrated in the accompanying drawings, since the invention is capable of other embodiments and of being practiced or carried out in various ways. Also it is to be understood that the phraseology or terminology employed herein is for the purpose of description and not of limitation;

Referring now to Figs. 1 and 2, it will be observed that an impeller 2 is fixed to a driving shaft 4 in any suitable manner as by means of a key 6. The driving shaft 4 may be driven by any suitable source of power such for example as the engine of a motor vehicle.

A driven shaft 8 having a turbine web l8 fixed thereto receives energy from fluid circulated by the impeller 2 and transmit the energy to the driven shaft 8. A guide wheel I2 is interposed between the turbine and impeller units to increase the turning moment of the fluid circulating through the impeller and turbine units.

The impeller, turbine and guide wheel provide a circuit in which fluid circulates to transmit power. The impeller 2 has a channel it between an impeller shroud l6 and an impeller web l8. The turbine has a channel 28 between a turbine shroud 22 and the turbine web l0 and the guide wheel has a channel 24 between a guide wheel shroud 26 and a guide wheel web 28.

The guide wheel web 28 is mounted for rotation on a sleeve 30 supported for rotation on the driving shaft 4, and a one-way drive mechanism 32 of any suitable type is interposed between the web 28 and the sleeve 38 to lock the guide wheel against rotation in clockwise direction as viewed in Fig. 2 when the transmission is operating as a torque converter and to permit the guide wheel to rotate in the counter-clockwise direction as viewed in Fig. 2 when the transmission is operating as a fluid coupling.

A case 34 on the sleeve 30 rotatable on the driving shaft 4 encloses the impeller, turbine and guide wheel, and the driven shaft 8 projects from the case 34 as illustrated. It will of course be understood that thecase 33 may be made in two or more parts to facilitate assembly. Any suitable one-way brake mechanism 36 may be interposed between the case 34 and a stationary portion 38 of the vehicle or other mounting of the device. When the transmission is operating as a fluid coupling, the one-way brake mechanism 36 operates to release the housing 34 to permit it to rotate with the turbine and impeller units so as to minimize friction.

A plurality of spaced semi-free vanes 40 are mounted on spaced shafts 42 in the entrance portion of the impeller channel M to vary the angular flow of the fluid as it enters the impeller. The vanes 40 are free to move angularly between limits defined by spaced stop members 44 arranged on opposite sides of the vanes and a plurality of flexible main blades 46 are preferably mounted on shafts 48 in the impeller channel I4 posterior to the semi-free vanes 40.

A plurality of spaced semi-free entrance vanes Bilmounted on shafts 52 Journaied in the turbine shroud 22 and the turbine web It) are in the entrance of the turbine channel 20. The vanes 50 are free to move angularly between limits defined by spaced stop members 54 arranged on opposite sides of the vanes, and a plurality of spaced main turbine vanes 53 are arranged in the turbine channel 20 posterior to the semifree vanes 58. a

A plurality of spaced main gates 58 fixed to spaced shafts 60 Journaled in the guide wheel shroud 26 and the guide wheel web '28 and extended through and beyond the web, are pro vided to vary the angular flow of the fluid in the guide wheel. Means are provided to vary the angular relation of the main gates 58 Within the channel 24.

One desirable control means for the gates comprises a plurality of pinions 62 one secured to each of the shafts 60 and meshing with a ring gear 64 rotatably mounted on a flange 66 carried by the guide wheel web member 28. A retainer 68 may be boltedto the flange 66 to secure the ring gear 64 against displacement. Yielding means such for example as a spring 70 is interposed between the ring gear 64 and the guide wheel web 28 to exert a yielding force on the ring gear 64 tending to urge the gates 58 toward one extreme angular position.

Fig. 3 shows an embodiment of the invention which is similar in many respects to that illustrated in Figs. 1 and 2. Corresponding parts have therefore been given corresponding reference numerals with the addition of 100. It will be observed that the guide wheel is provided with semi-free entrance gates I58a mounted on spaced rotatable shafts Mile. The gates l58a are movable angularly between the limits defined by Spaced stop members [60b on opposite sides of the gates.

Attention is called to the fact that this construction is disclosed but not claimed in my application Serial No. 475,278, now Patent No. 2,- 186,025, granted January 9, 1940, reference being had to Figs. 7, 8 and 14.

The construction disclosed in Figs. 4 and 5 originated for the most part in my application Serial No. 547,256, filed June 27, 1931, now Patent No, 2,271,919, dated February 3, 1942, as Figs. 26 and 27. It will be observed that a driving shaft l is provided to constantly drive a discharge impeller web 3 having an impeller channel 5 in which an impeller main blade I ispositioned. A case 9 is provided with a sleeve II which rides on a sleeve l3 of the impeller web 3 and supports an entrance impeller channel [5 having therein a plurality of spaced semifree vanes 11 mounted on rotatable shafts l9. Spaced stops 2| are provided to limit the angular movement of the semi-free vanes. ll.

Any suitable one-way driving means as illustrated diagrammatically by the pawl and. ratchet mechanism 23 and 25 may be provided to drive the case 9 having therein the entrance impeller channel l5, with the web 3 having therein the discharge impeller channel. 5. The one-way driving means may be controlled centrifugally to rotate the casing 9 with the web 3 when a substantially predetermined speed of rotation of the impeller is attained, suitable yielding means such as a spring 1| (Fig. 5) being provided to maintain the one-way driving means inoperative until a substantially predetermined speed of rotation is attained.

A discharge turbine channel 21 is supported by a ,web 20 fixed to am... shaft an, and an entrance t u'bine channel 22 is provided bye.

' accuses web '35 operably connected to the web 28 by any suitable one-way driving meansas fill-I89 trated diagrammatically by the centrifugally ac tuated ratchet and pawl. mechanism]! and 30.

respectively opposed by suitable yielding means such for exampleas a spring I9, illustrated in Fig. 5. I

A web 4I' mounted onthe driven shaft 3| has a discharge guide wheel channel 42 preferably adjacent the inlet impeller channel It Any suitable one-way brake such for example as the one-way brake, illustrated at 45' interposed between a sleeve 41 on the web and a stationary portion 49 of the vehicle may be provided to hold the web ll and the discharge guide wheel channel 43 when the transmission is operating as atorque converter and to release it when the transmission is operating as a fluid coupling.

An entrance guide wheel channel 5| provided by a web 53 is supported for rotation on a sleeve 55 integral withthe web 4|. Any suitable oneway driving means such'for example as that illustrated at 51 may be interposed between the web 53 and the sleeve iii to lock-the entrance and discharge guide wheels together when the transmission is operating as a torque converter eration results.

and after the portion III! of the portion 2 relieves the fluid pressure and equalizes fluid velocities on opposite sides of the blade whereupon less turbulence in the fluid flow is encountered and greater. efficiency of op- Figs. 9, l0 and 11 illustrate another desirable modification of impeller blade shown in the posi- I tions assumed at high, medium and idling speeds.

It will be observed that this blade has a main bodysection I! mounted on stationary shafts ll by means of a layer of resilient material 81 such is preferably of a relatively light material such for example as an alloy of aluminum and is' provided with a trailing portion .89, formed of heavy metal suchfor example as iron. or steel to increase the centrifugal force acting on. the I .blade to more accurately control the position and to release the guide wheels when the trans mission is operating as a fluid coupling. 7 A plurality of spaced main gates 59 interposed in the discharge guide wheel channel 43 may be provided to vary the anguiarity of the fluid flowing through the channel. The gates 59 may be mounted on rotatable shafts 8| having pinions 63 in mesh with a ring gear 84 to vary the angular relation of the main gates 58, yielding means such as a. spring 61 being interposed between the ring gear 65 and theweb 43 to yieldingly urge'the gates toward one extreme angular position. 7

Figs. 6, 7 and 8 illustrate a modification of an impeller blade which may be used in connection with the impellers disclosed in Figs. 1, 3 and 4. It will be observed that impeller blades I3 are fixed to shafts 16. The ends of the shafts I! are each provided with a slot "II. as illustrated in Figs. 7- and 8 to receive a flexible band 18 which yieldingly urges the vanes I5 toward the dotted line position 8| illustrated in Fig. .6. When the vanes I3 are in the dotted line position 8i the energy imparted to the fluid circulating in the unit is minimized whereupon pracv yielding force urging the vanes towards the dotted line position 8 I p 1 The inlet portions Hill of the vanes It are provided with scooping portions I02 defined by diverging angular walls I04. The surfaces I04 terminate in a body portion I06 of any desired fluid deflecting form and the trailing edges of the vanes terminate in portions I08 and the trailing edge IEO defined by angularly related surfaces II2.

The leading ends of the vanes I3 provide more efficient scooping or picking up of the fluid by the impeller.

Maximum energy is imparted to the circulating fluid by the body portion I06 of the blades under varying speeds of operation,

Suitable fixed entrance blades 9| may be pro-' vided to limit the angular movement of the main I blades in one direction when operating at high speed and to guide the'fluid into the impeller. It will be observed that in the medium' speed position illustrated in Fig; 10, the fluid may pass on both sides of the body section 83 whereupon the force required to drive the fluid is decreased. The resilient material 81 interposed between the body section 83 and the shafts 85 tends to yieldingly urge the vanes toward the idling position illustrated in Fig. 11. v I

The flxed entrance blades 9| are provided with angularly disposed surfaces I20 to pick up the power transmitting fluid and transmit it to the main body portion I22 in the manner discussed in connection with the bladeillustrated in Figs;

6 to 8. The outer edgev of the fixed entrance blades Si is angularly disposed as illustrated at I24 to coincide with leading edge I26 of the main body 83 when the vane 83 is in the high speed position as illustrated in Fig. 9.

The trailing edge of the blade 83 is defined by contoured surfaces providing a suitable outlet I28. A curved portion I30 interposed between the portion I28 and the main body I32 of the blade 83 is. most eflective in imparting energy to the circulating fluid as the impeller rotates. i

At idling speed as illustrated in Fig. ll the curved portion of the fixed entrance blades 9| readily scoops up the power transmitting fluid and transmits it to the contoured surfaces I22. The main blade 83 at idling speed occupies the substantially circumferential position illustrated in Fig. 11 under the influence of the force exerted bythe resilient material 81 interposed between the shafts 85 and the blades 83'. The

fluid picked up by the entrance blades 9i flows.

over theangularly disposed surface I24 and flows between the fixed entrance blades Ill' and the body sections I32 of the main blades 83.

. As the speed of rotation of the impeller increases, the trailing portion 89 being heavier than the leading portion I34 moves the blade 83 angularly on'the shaft 85 thereby flexing the the vane is As the speed of rotation is further increased with the corresponding increase in centrifugal force exerted on the trailing portions 88, the vanes 88 are rotated on the shafts 85 to assume the position illustrated in Fig. 9 whereupon the space between the entrance blades 8I and the leading edge I28 or the main blades 83 is closed to interrupt the flow of fluid therebetween. Under these conditions of operation, fluid flows along the surface of the fixed entrance blades and over the surface of the main blades, energy being imparted to the fluid as it is forced over the vanes -by rotation of the impeller. The maximum energy is imparted to the fluid at the curved portion I88 and afterpassing this point the velocity of the fluid is decelerated by the contoured surfaces I28 of the blade.

During idling speed operations as illustrated in Fig. 11, a space I38 is available between the fixed entrance blades 8| and the main blades 83 to equalize pressures on opposite sides of the blades.

Fig. 12 illustrates a modification of main vane 95 and semi-free vane 93 which may be employed in connection with an impeller, turbine or guide wheel unit. The resilient material 81 may be similar to that illustrated in connection with the embodiment of Figs. 9 and 11 and preferably operates to yieldingly urge the vane 83 to a position intermediate the full and dotted line positions wherein the trailing edge of the vane 88 lies approximately midway between the main vanes 85. It will be observed that as the vanes 83 are urged from the normal position by the fluid reaction they engage the blades 95 whichact as stop members to limit their angular movement.

to that of Fig. 12 with the exception that the alternate semi-free vanes 83 are free to move over a greater angle, the resiliency of the material 81 being relied upon to limit their extreme angular movements. Attention is called to the fact that as these vanes move angularly on the shafts 85, the parts do not wear because of the fact that there is no sliding movement since the material 8'! merely yields to permit the vanes to change their angular position.

Fig. 14 illustrates main turbine vanes 88 resiliently mounted on shafts as by rubber bushings 84, It will be observed that the main turbine vanes 88 are provided with flexible portions 88 at the trailing edges of the vanes which may be formed of any suitable yielding material and may be cast into the body portion of the vanes 88. As the vanes 88 move'angularly from the full line position toward the dotted line position, it will be observed that the entrance angle is increased and that the discharge angle is decreased whereupon a greater proportion of energy will be absorbed by the turbine wheel. The turbine wheels are thereby changed from antireaction vanes in the position shown in full lines to reaction vanes as illustrated in the dotted line positions.

Itwill be noted that the vanes 88 have well rounded entrance portions I48 andare of the high curvature type in order to absorb in the turbine the maximum torque from the power transmitting fluid. The blades are relatively thick adjacent their midportions I42 and taper to provide curved portions I44 to relieve the fluid velocity and equalize pressure adjacent the outlet from the turbine.

The trailing portions 88 of the vanes 88 being flexible are free to deflect the fluid to equalize the Fig. 13 shows an embodiment which is similar fluid pressures and velocities in the power transare free to seek the most efllcient operating position under the influence of forces exerted on their surfaces by the fluid flowing over their lower and upper surfaces I48 and I48 respectively.

Fig. 15 illustrates a still further modified form or a semi-free vane 88 suitable for use on an impeller. It will be observed that during a heavy load operation a main blade 88 and the semi-free vane 88 are in the position illustrated in full lines. As the speed increases at light load the semi-free vane 88 is moved by fluid reaction to the dotted line position, and'the blade 88 is moved by fluid reaction and centrifugal force to the dotted line position illustrated.

The semi-free vanes 88 being formed of resilient material and mounted on shafts I58 assume the dotted line position underno load condition. The main blades 88 are formedof resilient material and are mounted in a support I52 contoured to form a streamlined entrance edge portion I54 with respect to the body portion I58 to guide the fluid flow in such a manner as to minimize turbulence as the power transmitting fluid passes over the blades.

As the speed of rotation decreases and the load increases, fluid reaction exerted on the angularlyv disposed surfaces I58 and I88 of the semi-free vanes 88 induces them to move toward the full line position, and fluid reaction exerted on the opposite sides I82 and I84 of the main blade 88 causes them to assume the full line positions illustrated whereupon maximum energy is imparted to the circulating fluid.

It will be understood that the resilient mounting I52 is free to flex under the influence or centrifugal force and fluid reaction exerted on the surfaces I82 and I84 of the main' blades 88 whereby these blades act in a manner generally similar to the resilient mountings for the blades illustrated in Fig. 14.

Fig. 16 illustrates a turbine vane 92 of a deslrable fluid foil type mounted on a shaft 82 and having the flexible material 84 interposed therebetween. I

Fig, 17 shows an impeller blade 84 having a flexible trailing edge 88 cast in the body section 84 and mounted on a. shaft 98 with suitable resilient material interposed between the shaft and the body portion of the vane to permit varying the angular relation of the vane in accordance with the varying fluid forces exerted on the vane.

The impeller blade 84 has an under-bent portion I18 adjacent its leading edge to receive the power transmitting fluid in a more eiflcient manner and transmit it over the surfaces I12 and I14 of the blade 84, to a curved portion I18 wherein the maximum velocity is imparted to the energized fluid. The flexible trailing edge 88 of the blade 84 deflects under the influence of fluid reaction and centrifugal force to relieve the flow angles at the outlet from the blade 84 to equalize pressures and prevent turbulence.

Fig. 18 illustrates spaced turbine or guide wheel blades I88 having a plurality of rectifying vanes I82 interposed between each of the main vanes. The main vanes have leading edge portions I84 converging with streamline surfaces I 88 and I 88 of the main body portion I 88.

The trailing edges or the blades I88 are contoured to provide sections I82 and I84 to absorb from or impart maximum energy to the circulating fluid. The trailing edges of the blades beyond the portions I92 and I94 are curved as illustrated at I96 and I98 to equalize fluid velocities and pressures.

The rectifying vanes I82 interposed between each pair of main vanes I80 cooperate with the contours of the main blades I 80 to redirect the therefore desirable to employ the portions I96 the mime within the fluid channel. and connecting' means between the pintle and vane including rubber vulcanized to the pintle and vane to permit appreciable movement or the blade under the influence of the force exerted by the fluid circulating in the channel.

. 3.1n a fluid transmission, a pintle across a fluid channel, a, resilient sleeve fitted. on and bonded to the pintle so as to totally enclose the portions I92 and I94 of the blade I80 audit is and I98 to equalize fluid velocity and pressure to prevent turbulence.

- prevent creep., It is also to be understood that various features disclosed in the difierent figures of this application may be combined with corre sponding features of other figures without departing from the spirit of the invention.

It thus appears that the I trailing edge portion will minimize or eliminate-- turbulence in the power transmitting fluid imparted thereto by the fluid deflecting portion of I 'canized on the sleeve.

This application is a ocntinuation in-part of.

my co-pending application Serial No. 310,786,

flled December 23, 1939,- now abandoned, and a continuation in part of my co-pending applioation Serial No. 317,637, filed February 7, 1940, now Pat. No. 2,388,849.

I claim: 1. In a fluid transmission, a tending through the width 0! the blade and enclosed thereby, connecting means between the pintle and blade includingfflexible'materlal bonded to the pintle and blade wherebythe blade,

may move appreciably relative to the shaft. 1

2. In a transmission having a channel for the circulation of fluid, a pintle extending across said channel, a vane totally enclosing the portion ot v blade, 9. pintle ex- Number Name Date 110,915 Hawkins Jan. 10, 1871 1,825,768 Barbarou Oct. 6, 1931 1,942,721 Moflitt Jan. 9, 1934 2,168,862 De Lavaud Aug. 8, 1939 2,169,849 Pitcairn Aug. 15, 1939 2,186,025 Jandasek Jan. 9, 1940 2,200,596 1 Dodge May 14, 1940 2,235,370 Jandasek Mar. 18, 1941 2,235,605 Bugatti Mar. 18, 1941 2,245,251 Chilton June 10, 1941 "2,271,919 Jandasek Feb. 3, 1942 2,293,766 Salerni Aug. 25, 1942 FOREIGN PATENTS Number v Country Date Q 332,927 Germany 1,. Febx14, 1921 617,173 Germany ....Aug.13,l935

OTHER REFERENCES portion of the pintle in the channel, and a blade fitted on and bonded directly to the sleeve so as to totally enclose the sleeve.

- 4. In a fluid transmission, sleeve enclosing the pintle and vulcanized on the pintle, and a blade enclosing the sleeve and vul- Josnpn 'JANDASEK,

nnnannucas orran The following references are of record in the flle of this patent:

' UNITED STATES PATENTS 425,692, published June 1, 1943.

apintle, a rubber Publication DAubarede, Ser. No 

